EP1715216A2 - Amortisseur de vibrations torsionelles - Google Patents

Amortisseur de vibrations torsionelles Download PDF

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Publication number
EP1715216A2
EP1715216A2 EP06007655A EP06007655A EP1715216A2 EP 1715216 A2 EP1715216 A2 EP 1715216A2 EP 06007655 A EP06007655 A EP 06007655A EP 06007655 A EP06007655 A EP 06007655A EP 1715216 A2 EP1715216 A2 EP 1715216A2
Authority
EP
European Patent Office
Prior art keywords
spring system
torsional vibration
vibration damper
damper according
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06007655A
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German (de)
English (en)
Other versions
EP1715216A3 (fr
EP1715216B1 (fr
Inventor
Hartmut Bach
Thomas Dögel
Igor Kister
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP1715216A2 publication Critical patent/EP1715216A2/fr
Publication of EP1715216A3 publication Critical patent/EP1715216A3/fr
Application granted granted Critical
Publication of EP1715216B1 publication Critical patent/EP1715216B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/162—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material with forced fluid circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/137—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs the elastic members consisting of two or more springs of different kinds, e.g. elastomeric members and wound springs

Definitions

  • the invention relates to a torsional vibration damper according to the preamble of claim 1.
  • the DE 102 56 191 A1 is a torsional vibration damper with a drive-side transmission element, a respect to the same about a substantially identical axis of rotation battinghausable output-side transmission element and provided between the two transmission elements damping device known.
  • the drive-side transmission element is connected to a drive, such as a crankshaft of an internal combustion engine, while the output-side transmission element via a coupling device, for example by an engageable or disengageable friction clutch, with an output, such as a transmission input shaft, can be brought into operative connection.
  • the damping device is both with a gas spring system, comprising a A plurality of gas springs, and an auxiliary spring system, comprising a plurality of steel springs, provided for transmitting a torque between the drive-side and the driven-side transmission element.
  • a gas spring system comprising a A plurality of gas springs
  • an auxiliary spring system comprising a plurality of steel springs, provided for transmitting a torque between the drive-side and the driven-side transmission element.
  • the steel springs deform in a known manner by deformation in torsional vibrations hard shocks each in a softer vibration process
  • the gas springs are used to a damping process in which impact energy is dissipated.
  • the gas springs each have a gaseous medium, such as air, containing storage space within a cylinder chamber, said gaseous medium is pressed out upon compression of the gas springs and consequent volume reduction of the storage space via a throttle opening from the storage space. Understandably, upon release of the gas spring and the associated increase
  • the invention has the object of providing the damping device of a torsional vibration damper in such a way that unwanted buzzing noises are avoidable even under extreme conditions.
  • the partially active gas spring systems therefore have, compared to the fully active systems, because of the significantly reduced number of control operations with limited requirement for high readjustment speed over the advantage of working with respect to the fully active systems lower flow rates in the displacement of gaseous medium between the pressure circuit and the storage space can.
  • semi-active gas spring systems are characterized by low energy consumption and the requirement of only limited capacity storage for gaseous medium or even by the total abandonment of memory. Low can be in partially active gas spring systems, the pump power, in pumping operation can satisfy about 500 watts.
  • control a control and / or regulating device, hereinafter referred to as "control”
  • this rule For example, fall back on stored in the vehicle control operating points and therefore always a respective vehicle and / or driving condition relevant conditions associated supply of the storage space with gaseous medium, such as air, effect. Due to the thus contained in the storage space overpressure relative to the environment of the torsional vibration damper in each case the adjustment of the characteristic of the gas spring system.
  • the pressure in the storage space can be raised to a level or maintained at a level at which a relative rotational movement of the mutually rotatable transmission elements of the torsional vibration damper is at least largely avoided. Damage to the damping device is thereby effectively avoided.
  • the additional storage space is associated with a vibrating compressor.
  • this oscillating compressor it is possible to selectively generate gas pressure fluctuations in order thereby to assist relative movements between a cylinder chamber comprising the storage space and a piston of the gas spring system in overcoming the effective friction.
  • This advantage can be expanded by the oscillating compressor with the appropriate control of the same by the control functionality in the sense of a short path effective, complementary pump is generated, and thus an increase in pressure in the storage space and additional storage space can be achieved, regardless of the actual pump and / or co-operating with gaseous medium storages.
  • the oscillating compressor In addition, frequent changes in the stiffness of the gas spring system can be achieved by the oscillating compressor by means of gas pressure fluctuations, with which the formation of a resonance on the torsional vibration damper can be suppressed. Should nevertheless form a resonance, the oscillating compressor is advantageously associated with an actuator, preferably designed as a valve, for performing of regulation functions is connected to the control. If this actuator is closed at resonance or at least strong load changes, a pressure level remains unchanged in the gas spring system, which simulates a high rigidity and thereby prevent maximum relative rotational deflections between the two transmission elements.
  • the oscillating compressor can be designed as a reciprocating compressor.
  • the advantage of an assignment to the drive is the limitation to only one rotary feedthrough.
  • This can for example be formed in a flange of a rotary part of the drive, so the crankshaft, wherein in the flange of the crankshaft, a bore for passage of gaseous medium is provided in the drive-side transmission element of the torsional vibration damper and thus in the gas spring system.
  • a supply line assigned to the drive-side transmission element can be used.
  • the first rotary feedthrough can, in order to bridge the relative rotational movement of the output with respect to the stationary pressure circuit, be provided on the output side of a gearbox that serves to change the gear ratio, provided that the output completely penetrates the gearbox axially.
  • this rotary feedthrough may be provided in the clutch bell and thus on the drive side of the gearbox.
  • the second rotary feedthrough is preferably centered by the drive-side transmission element in order to be effective in turn by means of integrated bearing and / or sealing elements with respect to the output as a same with respect to the drive centering pilot bearing.
  • the pressure circuit connected to the gas spring system preferably has a supply reservoir, which can be filled by a pump with gaseous medium in a predetermined density. Because of this supply memory, it is possible very short notice an increase in pressure in the storage space and / or, if there is an additional storage space between the storage space and the supply storage, also of the latter cause, this increase in pressure associated with assignment of an actuator, such as a valve to the supply storage, can be influenced. For this purpose, however, a valve is appropriate whose flow is influenced by the regulation of the pressure circuit.
  • the pressure circuit can be designed as a closed or open supply system.
  • a closed supply system there is a pressure reduction in the storage space and / or, if there is an additional storage space between the storage space and the supply storage, also the same in an expanded memory, in an open supply system from the pressure circuit out in the atmosphere referred to below as "environment".
  • an actuator such as a valve is provided between the storage and / or additional storage space and the expanded storage or the environment, with a valve is useful here, the flow rate can be influenced by the control of the pressure circuit.
  • Another such actuator is present in a closed supply system, for adjusting the volume flow of gaseous medium between the expanded storage and the supply storage, wherein the compression of the expanded storage leaving medium before being fed into the supply storage by the intermediate pump, which compensate only a leakage losses Aspiration of gaseous medium from the environment sucks.
  • the latter actuator is dispensable, since all of the supply medium supplied to the gaseous medium is sucked from the environment and compressed by the pump.
  • the advantage of the closed supply system lies in a lower energy consumption, while the open supply system saves on the expansion storage.
  • the gas spring system which has gas springs, is advantageously used in combination with an additional spring system in which preferably steel springs are used.
  • the gas spring system, as well as the additional spring system, with the drive-side transmission element and / or the output side transmission element are operatively connected, and preferably in series with each other, wherein the gas spring system is advantageously by means of an intermediate transfer element with the additional spring system in operative connection.
  • the gas spring system is determined to transmit higher torques than the additional spring system.
  • the gas spring system can be arranged here with axial offset relative to the additional spring system. In the arrangement of the gas spring system operatively between the drive-side transmission element and the intermediate transfer element takes place until reaching a predetermined torque level of the torque supplied by the drive transmission via the output side provided additional spring system, wherein the gas spring system remains at least substantially undeformed. In this operating state, the mass moment of inertia of the drive-side transmission element is increased by the gas spring system. If the torque of the drive increases beyond this predetermined torque level, the additional spring system, which has then consumed its spring travel, will rotate together with the output-side transmission element, thereby increasing its mass moment of inertia. This leads, because of the calming of the output, to a better decoupling. A transmission of the torque is then exclusively via the gas spring system.
  • the gas spring system can be arranged at least substantially with radial offset relative to the additional spring system.
  • the arrangement of the gas spring system is substantially radially outside of the additional spring system. This has the advantage that the gas spring system serving to transmit the higher torques is arranged on a larger diameter relative to the additional spring system.
  • the respective cylinder chamber of a gas spring system is associated with a piston, in particular in this case its piston ram, bridging throttle connection, which can be influenced with respect to their throttling effect by means of an actuating element, the latter being adjustable according to specifications of the control.
  • This throttle connection extends substantially between two each filled with gaseous medium chambers of the cylinder chamber, which is preferably a piston rod chamber on one side of the piston ram as the first chamber, and the storage space on the opposite side of the piston ram.
  • the throttle connection can remain closed with preference, so that no pressure equalization between the two chambers of the cylinder chamber takes place.
  • the throttle connection itself can either be integrated in the cylinder chamber, or run outside it, for example in the form of a line.
  • the adjusting element for setting the respective throttling action is preferably designed as a valve which is either passive, that is not adjustable, but with greater preference active, so for example via the control is adjustable, and with particular preference amplitude-selective, ie in association with Strength of the respective rotation angle deflection between the two transmission elements.
  • the gas spring system advantageously has a filled with viscous medium pressure chamber, which extends between the piston plunger and a pressure chamber from the storage space insulating separating piston.
  • the viscous medium of the pressure chamber ensures on the one hand for an optimal sealing of each filled with gaseous medium chambers, ie piston rod space and storage space against each other, and on the other hand for a permanent lubrication of the piston associated seal.
  • the lubrication of the seal essentially has the meaning, the "breakaway torque" of the seal, so that moment from which the piston no longer adheres due to friction on the seal on the associated cylinder wall, but dissolves from the same, to minimize.
  • the already mentioned oscillating compressor can serve the same purpose by producing a correspondingly "pulsed", ie vibrating column of gaseous medium, whereby the adherence of the piston plunger to the seal on the cylinder wall is to be prevented.
  • the pressure circuit of the gas spring system is preferably associated with a plurality of stores, such as a supply store or an expanded store.
  • a plurality of stores such as a supply store or an expanded store.
  • the energy contained in the gas spring system can be stored not only substantially lossless, but also continuously retrieve in a very short time or continuously deliver.
  • these memories may be due to Arbitrarily possible design anywhere on a vehicle, mainly this outside of the torsional vibration, arrange, so that an excellent use of space is guaranteed.
  • Inexpensive and technically unproblematic is the gas spring system, in particular when already existing technology in the vehicle can be used.
  • a compressor which can be used as a pump for the pressure circuit, but otherwise is already present because of the air conditioning system of the vehicle and / or because of a suspension configured with variably adjustable damping.
  • the drive 1 and 2 show a torsional vibration damper 2, which, as is apparent from Fig. 1, to be rotatably connected to a drive 1.
  • the drive 1 is preferably designed as an internal combustion engine, in which a housing 157 as Stationary part 155 of the drive 1 and a crankshaft 3 as a rotary part 156 of the drive 1 is used.
  • 1 further schematically shows a bearing 160, by means of which the rotary part 156 is centered substantially friction-free with respect to the stationary part 155, wherein the bearing 160 is intended to represent the bearing element of a plurality of bearing elements of the drive 1 which is not axially closest to the torsional vibration damper 2.
  • the torsional vibration damper 2 For rotationally fixed connection of the torsional vibration damper 2 to the crankshaft 3, the torsional vibration damper 2 has a crankshaft 3 adjacent radial flange 5, which merges im.radial outermost region in a sprocket 9 carrying axial approach 7.
  • the radially inner region of the radial flange 5 serves in a manner not shown for connecting the torsional vibration damper 2 to the crankshaft 3
  • the radially outer region of the radial flange 5 is provided for receiving a gas spring system 14, which will be explained in detail below with reference to FIG.
  • the radial flange 5 is connected via a molded drive-side primary drive element 16 with a cylinder chamber 12 of the gas spring system 14 in operative connection.
  • a gas spring system 14 should also be used in the latter half of the picture.
  • the gas spring system 14 accommodates in its cylinder chamber 12 a piston 17 with a piston rod 18 which extends into a piston rod chamber 20.
  • the piston 17 further has a piston ram 25, which is at least substantially adapted with its piston ram edge 24 with respect to its geometry to the cross-sectional shape of the cylinder chamber 12, wherein the embodiment of FIG. 1 or 2 of a substantially circular cross-sectional configuration of piston ram 25 and cylinder space 12 goes out.
  • the piston 17 engages with its piston rod 18 in the circumferential direction a recess 23 of a seal 22 which is provided on the piston rod side of the piston ram 25.
  • the circumference opposite side of the piston ram 25 limits a provided in the cylinder chamber 12 pressure chamber 27, whose circumference other boundary is formed by a separating piston 30 which in turn with its side remote from the pressure chamber 27 side memory space 32 of the cylinder chamber 12 limited.
  • a supply line 34 which, as shown in FIG.
  • the additional spring system 50 is supported by sliding guides 54 radially outward on a provided on the receiving space 48 guide path 56 and applied with its remote from the drive side secondary drive elements 49 peripheral side a hub disc 57, which therefore effective as output side secondary drive element 58 and by means of a Nabenusionnfußes 59 on the Radialflanschnabe 26 is arranged.
  • This hub disc 57 in turn rotatably carries a ring mass 60, in which axial passages 61 are provided for receiving a connection to the hub disc 57 producing riveting 62.
  • the friction clutch 70 is formed with a diaphragm spring 72, whose Control for engagement or disengagement by means of a disengager, not shown, via their radially inwardly gripping spring tongues 73 takes place.
  • the clutch disc 78 has in the radially inner region via a hub 80 which via a toothing 82 axially displaceable, but rotatably on a transmission input shaft 84 engages, which either forms the output 86 or is assigned to the same component.
  • a drive-side transmission element 88 of the torsional vibration damper 2 is formed by the radial flange 5 inclusive of the supply line 34 and the gas spring system 14, an intermediate transfer member 90 of the torsional vibration damper 2 through the intermediate disc 38 and the receiving space 48 and through the hub disc 57 together with the ring mass 60 and the Friction clutch 70, a driven-side transmission element 92 of the torsional vibration damper. 2
  • each Axialdistanzstoff 94 is provided for a while elastic, but still predetermined relative position of the individual transmission elements 88, 90, 92nd should provide each other in the axial direction.
  • the torsional vibration damper 2 interacts with a pressure circuit 120, which is shown only schematically in FIG. 1 by means of a pressure connection 100. Further information on the design of the pressure circuit 120 will be given below with reference to FIG. 3 or 8. From Fig. 1, however, it can be seen that the supply line 100 of the pressure circuit 120 is in operative connection via a first pressure transfer point 95 with the transmission input shaft 84 and therefore with the output 86, and that the output 86 in the form of the transmission input shaft 84 in turn by means of a second pressure transfer point 96th is in operative connection with the supply line 32. Both pressure transfer points 95, 96 are, like the drive 1 and the output 86 are each aligned with respect to a rotational axis 99.
  • the latter has a first pressure circuit component 101, which connects to the supply line 100 with a radial passage 106 and, like the latter, at least substantially is stationary.
  • the transmission input shaft 84 Relatively rotationally movable relative to this first pressure-circuit component 101 is the transmission input shaft 84, which in turn finds a pressure connection with the first pressure-circuit component 101 with a first radial portion 102.
  • 106 position and / or sealing means 104 are provided axially on both sides of the radial passage, and that at the transmission input shaft 84 facing radial side of the first pressure circuit component 101.
  • the transmission input shaft 84 also serves as a pressure circuit component.
  • the radial section 102 of the transmission input shaft 84 is in pressure communication with a provided in the transmission input shaft 84, extending substantially in the axial direction central recess 108 in the form of an integrated pressure line 107, which merges in the region of the drive-side end of the transmission input shaft 84 in a further radial portion 110 of the transmission input shaft 84 ,
  • This radial section 110 is in pressure communication with a radial passage 112 in a second pressure circuit component 109 which, belonging to the second pressure transmission point 96, is again formed by bearing and / or sealing means 104 provided axially on both sides of the radial section 110 and the radial passage 112 the radial input of the second pressure circuit component 109 facing the transmission input shaft 84.
  • the second pressure circuit component 109 is at least substantially identical in movement to the supply line 34 and thus to the drive-side transmission element 88, so that a relative movement must also be assumed between the second pressure circuit component 109 and the transmission input shaft 84.
  • the first pressure transfer point 95 serves as the first rotary feedthrough 98 and the second pressure transfer point 96 as the second rotary feedthrough 114.
  • FIG. 9 shows the characteristic curves as a function of the respective torque M, relative to the deflection angle ⁇ provided by the gas spring system 14. The transition between the individual characteristic curves can be effected by predeterminable large steps or at least substantially continuously.
  • the overall characteristic curve of the torsional vibration damper 2 is shown in FIG. 10, and likewise as represented as a function of the respective torque M, relative to the deflection angle ⁇ provided by the gas spring system 14.
  • the characteristic in Fig. 10 is based on a vote, according to which the additional spring system 50 has only one characteristic which, until reaching a predetermined torque of the drive, recognizable in Fig. 10 by the critical angle ⁇ G, provides for the function of the torsional vibration damping , wherein up to this predetermined torque, the gas spring system 14 undergoes at least substantially no deformation.
  • the additional spring system has its entire available travel used up, so that from now on, starting with the critical angle ⁇ G, the previously explained with reference to FIG. 9 characteristic situation of the gas spring system 14 effects.
  • the piston rod chamber 20 enclosing the piston rod 18 can either be filled with gaseous medium, but can also be depressurized, which is briefly referred to below as the term "environment".
  • the respective environment carries the reference numeral 140 there.
  • a first actuator 122 adjoins the drive-side pressure transfer point 95, which is connected to a control and / or regulating device 125 and can therefore be influenced with regard to its setting, the control and / or regulating device 125 subsequently being short is designated as control 125.
  • the pressure connection to an additional storage space 132 is adjustable, which when the first actuator 122 is open, an increase in the Volume of the storage space 32 of the gas spring system 14 allows, with closed first actuator 122, however, excludes a volume influence of the storage space 32.
  • the additional storage space 132 as well as the supply line 100 is arranged stationary, even with critical space conditions for the torsional vibration damper 2 with its drive-side transmission element 88 moving storage space 32 are kept compact and instead the corresponding volume in the additional storage space 132 to be supplemented.
  • An even higher volume for gaseous medium in the storage space 32 and in the additional storage space 132 functions like an extremely large spring travel on a conventional steel spring torsional vibration damper, in particular by the additional storage space 132 of the travel can be increased without penalty.
  • an oscillating air column can be generated by the oscillating compressor 127, which further minimizes the previously mentioned friction-related adhesion of the piston 17 via its piston-piston rim 24 on the cylinder chamber 12.
  • the oscillating compressor 127 can also be used for an increase in pressure or for a pressure reduction in the additional storage space 132 and thus ultimately also in the storage space 32 with appropriate control, for example by means of the control 125, at least in the short term.
  • the additional storage space 132 is on the one hand via a second actuator 134 and a supply storage 136, in which a predetermined overpressure can be established, to a pressure outlet D of a pump 138th connected. Furthermore, the additional storage space 132 is connected via a third actuator 142, an expanded memory 144 and a fourth actuator 146 to a first suction inlet S1 of the pump.
  • the actuators 134, 142 and 146 are each connected to the controller 125 and thus adjustable with respect to their respective opening width. While the second actuator 134, the filling of the additional storage space 132 from the supply storage 136 with gaseous medium made adjustable, via the third actuator 142, the emptying of the additional storage space 132 can be set in the expanded memory 144.
  • the proportion of gaseous medium which reaches the pressure output D via the suction inlet S1 of the pump 138 can be determined relative to a further proportion of gaseous medium which is received via a second suction inlet S2 of the pump 138.
  • the pump 138 is effective as the compressed air source 170.
  • FIG. 3 While in FIG. 3 the pressure circuit 120 is designed as a closed supply system, in which only the losses of gaseous medium from the environment 140 are replaced, the pressure circuit 120 is in accordance with FIG. 8 shows an open supply system in which all of the gaseous medium leaving the additional storage space 132 is discharged to the environment 140, and also the entire gaseous medium to be supplied to the auxiliary storage space 132 via the supply storage 136 by the pump 138 is removed from the environment 140.
  • Fig. 4 shows a particular embodiment of the gas spring system 14, wherein between the storage space 32 and the piston rod chamber 20, a throttle connection 148 which can be adjusted by means of a control element 125 connected to the control element 150.
  • FIGS. 5 and 6 correspond, as far as the design of the gas spring system 14 is concerned, essentially to the embodiment according to FIG. 1, but offer other geometric cross-sectional shapes.
  • Fig. 5 shows a polygonal embodiment of the piston ram 25 and the piston ram rim 24 on the piston 17 and, in adaptation thereto, a likewise polygonal design of the cylinder chamber 12.
  • Fig. 6 represents an embodiment with elliptical geometry. Such geometries allow a optimal Adaptation of the gas spring system 14 to the space provided for the torsional vibration damper 2.
  • Fig. 7 shows a substantially deviating from Fig. 1 embodiment of a pressure transfer point
  • the reference numeral 151 is assigned in Fig. 7.
  • a first pressure circuit component 153 is present, which is at least substantially non-rotatable relative to the stationary part 155 of the drive 1, ie opposite the housing 157, while a second pressure circuit component 154 of the pressure transmission point 151 is substantially identical in movement with the rotation part 156 of the drive. 1 , So with the crankshaft 3 is.
  • a first pressure circuit component 153 is present, which is at least substantially non-rotatable relative to the stationary part 155 of the drive 1, ie opposite the housing 157, while a second pressure circuit component 154 of the pressure transmission point 151 is substantially identical in movement with the rotation part 156 of the drive. 1 , So with the crankshaft 3 is.
  • Relative movement between the two pressure circuit components 153, 154 bearing and / or sealing means 104 are provided, namely axially on both sides of a radial passage 163 which is included in the first pressure circuit component 153, and also axially on both sides of the radial input of a power supply 164 in the second pressure circuit component 154, wherein this supply deflection 164 opens into the supply line 34 of the gas spring system 14.
  • the second pressure circuit component 154 has a radially outwardly extending support flange 162, which serves for fastening of the radial flange 5 of the drive-side transmission element 88.
  • FIG. 7 differs from that according to FIG. 1 in that in FIG. 7 the intermediate disk 38 acted upon by the piston rod 18 of the piston 17 of the gas spring system 14 forms the intermediate transfer element 90 together with the hub disk 57, so that now the Hub disc 57 serves as a drive-side secondary drive element 49. Therefore, in this constructive embodiment, the output side secondary drive elements 58 for the additional spring system 50 will be provided on the cover plates 42 and 44. Consequently, the cover plates 42, 44 together with a coupling housing 68, which is connected to the output side cover plate 44 by means of a toothing 172 in axially displaceable, but rotationally fixed connection, as the output-side transmission element 92 is effective. Unlike in Fig.
  • the clutch housing 68 is preferred part of a coupling device not shown in detail, as used in conjunction with powershift transmissions.
  • a coupling device is known per se, for example by the DE 100 34 730 Al, and should therefore not be explained in detail.
  • the gas spring system 14 and the additional spring system 50 are arranged with axial offset relative to one another depending on the particular space requirements for the torsional vibration damper 2, or with radial offset relative to one another according to FIG.
  • the positions of the gas spring system 14 and the additional spring system 50 with respect to the drive-side transmission element 88 and the output-side transmission element 92 can be arbitrarily interchanged.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Vibration Prevention Devices (AREA)
EP06007655.1A 2005-04-23 2006-04-12 Amortisseur de vibrations torsionelles Not-in-force EP1715216B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005018954A DE102005018954A1 (de) 2005-04-23 2005-04-23 Torsionsschwingungsdämpfer

Publications (3)

Publication Number Publication Date
EP1715216A2 true EP1715216A2 (fr) 2006-10-25
EP1715216A3 EP1715216A3 (fr) 2016-01-13
EP1715216B1 EP1715216B1 (fr) 2018-07-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06007655.1A Not-in-force EP1715216B1 (fr) 2005-04-23 2006-04-12 Amortisseur de vibrations torsionelles

Country Status (4)

Country Link
US (1) US7604542B2 (fr)
EP (1) EP1715216B1 (fr)
JP (1) JP5037032B2 (fr)
DE (1) DE102005018954A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008080484A1 (fr) * 2006-12-22 2008-07-10 Zf Friedrichshafen Ag Ensemble amortisseur de vibrations de torsion
WO2008080485A1 (fr) * 2006-12-22 2008-07-10 Zf Friedrichshafen Ag Ensemble amortisseur de vibrations de torsion
EP1975477A1 (fr) * 2007-03-31 2008-10-01 ZF Friedrichshafen AG Passage tournant, en particulier pour un amortisseur d'oscillations de torsion dans un train d'entraînement d'un véhicule

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005058531A1 (de) * 2005-12-08 2007-06-14 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
GB0623292D0 (en) * 2006-11-22 2007-01-03 Zeroshift Ltd Transmission system
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DE102007054570A1 (de) * 2007-11-15 2009-05-20 Zf Friedrichshafen Ag Torsionsschwingungsdämpferanordnung
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EP1715216A3 (fr) 2016-01-13
JP5037032B2 (ja) 2012-09-26
US7604542B2 (en) 2009-10-20
JP2006300327A (ja) 2006-11-02
EP1715216B1 (fr) 2018-07-11
US20060247065A1 (en) 2006-11-02
DE102005018954A1 (de) 2006-11-02

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